WO2023071976A1

WO2023071976A1 - Heat exchange device

Info

Publication number: WO2023071976A1
Application number: PCT/CN2022/126995
Authority: WO
Inventors: 陈彦峰
Original assignee: 陈彦峰
Priority date: 2021-10-26
Filing date: 2022-10-24
Publication date: 2023-05-04
Also published as: TW202319700A; CN116019353A; CN220001490U

Abstract

A heat exchange device comprising a first fluid path. The heat exchange device is used for exchanging heat between first fluids (35A, 35B) inside the first fluid path and second fluids (36A, 36B) outside the first fluid path; the first fluid path is divided into a first channel and a second channel; at least part of the first channel is formed as part of a first heat exchanger (21) such that the first fluid (35B) in a gaseous state releases heat when flowing through the first heat exchanger (21), and at least part of the second channel is formed as part of a second heat exchanger (31) such that the first fluid (35A) in a liquid state flowing in the second channel absorbs heat; the first channel and the second channel are configured to have different air pressure values when the heat exchange device operates; the first fluid path is sealed in a heat exchange working state; the first heat exchanger (21) is provided with a first gas flow guide structure (219) for facilitating spiral flow of the first fluid (35B) in the gaseous state in the first heat exchanger (21); the second heat exchanger (31) is provided with a first liquid flow guide structure (320) for promoting spiral flow of the first fluid (35A) in the liquid state in the second heat exchanger (31); at least one of the first gas flow guide structure (219) and the first liquid flow guide structure (320) is movable. The heat exchange device reduces energy consumption, saves energy, and improves energy utilization.

Description

heat exchange device

technical field

The present application relates to energy transfer technology, in particular to heat exchange devices.

Background technique

Hot water has a wide range of uses in people's daily life, such as cooking, cleaning and so on. Generally speaking, in the scenario where hot water or warm water is used for cleaning, the discharged wastewater after cleaning still contains a lot of heat energy. These heat energy are often wasted along with the discharge of waste water, resulting in energy waste. Another example is when using hot water for cooking, it is generally necessary to heat the water to boil to cook the food, or to heat the water to generate water vapor to steam the food. However, high-temperature water vapor is generally discharged into the ambient air during or after cooking, and the boiled water after cooking is generally treated as waste water or naturally cooled. The steam contains a lot of heat energy, especially the latent heat absorbed by the liquid when it evaporates, as high as 2250KJ/Kg. In real life, these thermal energy are often wasted. All along, people try to adopt various methods to recover and utilize these lost and wasted energy.

US Patent No. US1025400713B2 discloses a steam cooking device A41 as shown in FIG. 1 , which includes a first heat exchanger A6 and a second heat exchanger A46. The first heat exchanger A6 is used to exchange heat between the liquid working fluid A21 (such as water) and the water vapor A53, so that the water vapor A53 releases heat and condenses, and the working fluid A21 absorbs the latent heat released by the condensation of the water vapor A53 to evaporate and gasify . The second heat exchanger A46 is used to exchange heat between the vaporized working fluid A21 and the aqueous liquid A45. The liquid is liquefied due to heat exchange and latent heat is released in the process, thereby heating and boiling the aqueous liquid A45 and generating water vapor A53 for heating the food 52. Although the cooking device can recover a part of heat energy through heat exchange, the following problems still exist in its recovery efficiency.

Specifically, as shown in Figure 1:

1) In the heat exchange at the first heat exchanger A6, first, a large part of the water vapor A53 will condense into water droplets after heat exchange and adhere to the fins of the first heat exchanger A6 or the outer wall of the pipe. Since liquid water droplets are not good conductors of heat, they will block the heat conduction between the water vapor A53 and the fins of the first heat exchanger A6 and the outer wall of the pipe, thereby reducing the heat exchange efficiency between the water vapor A53 and the working fluid A21 .

At the same time, the working gas bubbles formed by the vaporization of the liquid working fluid A21 are also attached to the inner wall of the pipeline of the first heat exchanger A6. Since the gas bubbles are not good conductors of heat, they will block the heat conduction between the liquid working fluid A21 and the inner wall of the pipe of the first heat exchanger A6, thereby reducing the flow of liquid working fluid A21 and water vapor A53 in the first heat exchanger A6. heat transfer efficiency at the place.

2) In the heat exchange at the second heat exchanger A46, first, the gaseous working fluid A21 will condense into a liquid state in the pipe after the heat exchange, and the generated liquid will adhere to the inner wall of the pipe of the second heat exchanger A46 . Since the liquid working fluid (for example, water) condensed on the inner wall is not a good heat conductor, it will block the heat conduction between the working gas and the inner wall of the pipeline of the second heat exchanger A46, thereby reducing the heat transfer between the working gas A21 and the water-containing liquid A45. Heat exchange efficiency at the second heat exchanger A46.

At the same time, when the water-containing liquid A45 absorbs the heat of the working fluid A21 in the second heat exchanger A46 and vaporizes, water vapor bubbles will be formed, and the bubbles will adhere to the fin surface and the outer wall of the pipe of the second heat exchanger A46. Since the water vapor bubbles are not good conductors of heat, they block the heat conduction between the aqueous liquid A45 and the working fluid A21 between the second heat exchanger A46, thereby reducing the heat exchange efficiency of the second heat exchanger A46.

It can be seen that the heat exchange efficiency in the above example is not very ideal, and there is room for improvement. In addition, the first heat exchanger A6, the valve A24, the compressor A22 and the second heat exchanger A46 are connected through pipelines to form a permanent closed flow path, and only water and water vapor exist in the flow path. When the device is at rest, its temperature cools to room temperature, at which point the water vapor in the closed flow path condenses into water, and the pressure inside the closed flow path drops to a near vacuum. This will result in the parts forming the closed flow path and their connections needing to withstand the pressure of about 1 BAR from the atmosphere for a long time when the device is at rest. This pressure is easy to damage the reliability and stability of the components of the device, which raises the performance requirements for the components delivered from the factory, and increases the cost of the device in a disguised form.

Based on the above reasons, there is a need in the prior art to improve the heat exchange efficiency of the heat exchange device and to improve the reliability and stability of the device.

Contents of the invention

The purpose of this application is to provide a heat exchange device, which can effectively solve the above problems, significantly improve energy recovery efficiency, and reduce the damage of atmospheric pressure to the device, improve the reliability, stability and service life of the device, and be easy to use .

According to a first aspect of the present application there is provided a heat exchange device comprising a first fluid path for a first fluid (35A, 35B) in the first fluid path and said first fluid path Heat is exchanged between an external second fluid (36A, 36B), the first fluid path is divided into a first channel and a second channel, wherein at least a part of the first channel is formed as a first heat exchanger ( 21) for releasing heat energy when said first fluid (35B) in gaseous state flows through said first heat exchanger (21), at least a part of said second channel forms a second heat exchange part of the device (31) such that said first fluid (35A) in a liquid state flowing therein absorbs thermal energy, wherein said first channel and said second channel are configured when said heat exchange device is in operation have different air pressure values, wherein the first fluid path is sealed when it is in the heat exchange working state, wherein the first heat exchanger (21) is provided with a device for promoting the first fluid in the gaseous state (35B) A first gas guide structure (219) for spiral flow in the first heat exchanger (21), wherein the second heat exchanger (31) is provided with a structure for promoting the The first liquid guide structure (320) in which the first fluid (35A) spirally flows in the second heat exchanger (31), wherein the first gas guide structure (219) and the first liquid guide structure At least one of the flow structures (320) is movable. Preferably, the first fluid path is not in fluid communication with a second fluid path located outside the first fluid path at the first heat exchanger (21) and the second heat exchanger (31), respectively. The heat exchange device is configured such that: the gaseous first fluid (35B) is mixed with the liquid second fluid in the second fluid path when flowing through the first heat exchanger (21) (36A) heat exchange such that at least a portion of the liquid second fluid (36A) is vaporized into said second fluid (36B) in gaseous state and at least a portion of said gaseous first fluid (35B) is condensed into The first fluid (35A) in a liquid state; the first fluid (35A) in a liquid state and the gaseous second fluid in the second fluid path when flowing through the inside of the second heat exchanger (31) fluids (36B) exchange heat such that at least a portion of said first fluid (35A) in liquid state is vaporized into said first fluid (35B) in gaseous state and at least a portion of said second fluid (36B) in gaseous state The second fluid (36C) is condensed into a liquid state. Preferably, at least a part of the first liquid guide structure (320) is adjacent to the inner wall of the second channel forming the second heat exchanger (31) and a spiral guide channel is formed along the inner wall, Wherein, at least a part of the first gas guide structure (219) is adjacent to the outer wall of the pipe (212A) forming the second fluid path in the first heat exchanger (21) and is formed along the outer wall Spiral channel. Preferably, the heat exchange device further includes a compressor (11) arranged in the first fluid path and a regulating valve (12) spaced apart from the compressor (11), and the first fluid path Divided into the first passage and the second passage by the compressor (11) and the regulating valve (12), wherein the compressor (11) and the regulating valve (12) are used to change the The air pressures in the first channel and the second channel are such that the first channel and the second channel have different air pressure values when the heat exchange device is in operation. Preferably, the heat exchanging device further comprises a first gas power device (213) for promoting the gaseous first fluid to circulate through the first heat exchanger (21) in the first channel. Preferably, said heat exchanging device further comprises a first hydrodynamic device (314) for promoting circulation of said first fluid in liquid state through said second heat exchanger (31) in said second channel. Preferably, the first fluid path can communicate with the outside world by selectively opening the gas valve (222) and/or the liquid valve (603). Preferably, the heat exchanging device further includes a first heating device (318) and a first chamber (315) located on the first fluid path, wherein the first chamber (315) is used to accommodate liquid the first fluid (35A), wherein the first heating device is used to heat the first chamber (315) to vaporize the first fluid (35) therein. Preferably, when the first heating device is used to heat the first chamber (315), the gas valve (222) is in an open state. Preferably, the heat exchange device further includes a second chamber (322) for collecting and containing the second fluid (36C) liquefied through the second heat exchanger, and the liquefied second fluid (36C) A second fluid can enter the first chamber (315) by opening the liquid valve (603).

According to a second aspect of the present application there is provided a method for transferring heat between a first fluid (35/36) and a second fluid (36/35) which is in a different state of matter from said first fluid before the heat exchange A heat exchanging device for exchanging, the heat exchanging device having a first heat exchanging channel (211/311) for passing the first fluid and a second heat exchanging channel (212) for passing the second fluid /312), at least a part of the second heat exchange channel is formed by the lumen of the pipe (212A/312A) having an inner wall and an outer wall, wherein the second heat exchange channel (212/312) is not fluid to each other The way of communication intersects with the first heat exchange channel (211/311) and passes through the first heat exchange channel (211/311), wherein the first heat exchange channel (211/311) is set There is a first flow guiding structure (219/319) that promotes the spiral flow of the first fluid (35/36) flowing through the first heat exchange channel around the second heat exchange channel, wherein the second heat The exchange channel (212/312) is provided with a second flow guide structure (220) that promotes the spiral flow of the second fluid (36/35) flowing through the second heat exchange channel in the second heat exchange channel. /320), at least one of said first flow guiding structure (219/319) and said second flow guiding structure (220/320) is movable, wherein at least a portion of said first fluid and said At least a portion of the second fluid changes state due to the heat exchange. Preferably, at least a part of the first flow guide structure (219/319) is adjacent to the outer wall of the pipe (212A/312A) forming the second heat exchange channel (212/312) and a spiral is formed along the outer wall shaped flow channels. Preferably, at least a part of the second flow guide structure (220/320) is adjacent to the inner wall of the second heat exchange channel (212/312) and a spiral flow guide channel is formed along the inner wall. Preferably, the heat exchange device further has a first fluid path for the first fluid to flow, and the first fluid path has a compressor (11) arranged in the first fluid path and communicates with the compressor ( 11) A spaced regulating valve (12), the first fluid path is divided into a first passage and a second passage by the compressor (11) and the regulating valve (12), wherein the first fluid The path is sealed when it is in the heat exchange working state, and the compressor (11) and regulating valve (12) are used to change the air pressure in the first channel and the second channel so that the heat exchange device operates When the first channel and the second channel have different air pressure values, wherein the first heat exchange channel (211) is formed by at least a part of the first channel. As preferably, the heat exchange device further includes the second fluid path through which the second fluid flows, the second fluid path is located outside the first fluid path, and communicates with the first fluid path intersect in fluid non-communicative manner, wherein the second heat exchange channel (212) is formed by at least a portion of the second fluid path. Preferably, at least a part of the second channel of the first fluid path forms a third heat exchange channel (312), and at least a part of the third heat exchange channel is formed by a pipe (312A) having an inner wall and an outer wall ), the second fluid path forms a fourth heat exchange channel (311) at the intersection with the third heat exchange channel (312) of the first fluid path, and the third heat exchange channel Channels (312) intersect and pass through said fourth heat exchange channel (311) in a manner not in fluid communication with each other. Preferably, the third heat exchange channel (312) is provided with a third flow guide structure (320) for promoting the spiral flow of the first fluid therein, and the fourth heat exchange channel (311) is provided with a useful A fourth flow guide structure (319) for promoting the spiral flow of the second fluid therein, wherein at least one of the third flow guide structure (320) and the fourth flow guide structure (319) is movable, wherein The first fluid and the second fluid exchange heat through the third heat channel and the fourth heat channel and cause at least a part of the first fluid and at least a part of the second fluid to change a physical state. Preferably, at least a part of the fourth flow guide structure (319) is adjacent to the outer wall of the pipe 312A forming the third heat exchange channel (312), and a spiral flow guide channel is formed along the outer wall. Preferably, at least a part of the third flow guide structure (320) is adjacent to the inner wall of the pipe 312A forming the third heat exchange channel (312), and a spiral flow guide channel is formed along the inner wall. Preferably, the heat exchanging device further comprises a first gas power device (213) for promoting the gaseous first fluid to circulate in the first channel through the first heat exchanging channel (211). Preferably, said heat exchanging means further comprises a first hydrodynamic device (314) for facilitating circulation of said first fluid in liquid state in said second channel through said third heat exchanging channel (312). Preferably, the first fluid path can communicate with the outside world by selectively opening the gas valve (222) and/or the liquid valve (603). Preferably, the heat exchanging device further includes a first heating device (318) and a first chamber (315) located on the first fluid path, wherein the first chamber (315) is used to accommodate liquid the first fluid (35A), wherein the first heating device is used to heat the first chamber (315) to vaporize the first fluid (35) therein. Preferably, when the first heating device is used to heat the first chamber (315), the gas valve (222) is in an open state. Preferably, the heat exchange device further includes a second chamber (322) for collecting and containing the second fluid liquefied through the fourth heat exchange channel, and the second fluid can be opened by opening The liquid valve (603) enters the first chamber (315).

From the following detailed description combined with the accompanying drawings, the principles, characteristics, characteristics, advantages, etc. of each technical solution according to the present application will be clearly understood. For example, compared with the prior art, the technical solution of the present application is easy to manufacture, install and maintain, has low cost of use, and can effectively ensure and improve the working performance, safety and reliability of the device due to adverse effects caused by condensation. This application has significant utility.

Description of drawings

The technical solutions of the present application will be described in further detail below in conjunction with the drawings and embodiments, but these drawings are provided for the purpose of explanation only, and are only intended to conceptually illustrate the structural construction here, and do not necessarily Manufactured to scale.

The basic structure of the present application is exemplarily described below with reference to the accompanying drawings, wherein:

Figure 1 is a prior art heat exchange device.

Fig. 2 is a schematic structural diagram of a heat exchange device according to an embodiment of the present application.

Fig. 3 is a schematic diagram of a first fluid path in the heat exchange device shown in Fig. 2 .

Figures 4A and 4B show the heat exchange at the first heat exchanger (21) in the heat exchange device shown in Figure 2 under the situation of not configuring the flow guide structure of the present application and configuring the flow guide structure of the present application respectively. time schematic diagram.

Figures 5A and 5B show respectively that the heat exchange at the second heat exchanger (31) in the heat exchange device shown in Figure 2 is not configured with the flow guide structure of the present application and configured with the flow guide structure of the present application time schematic diagram.

Detailed ways

First of all, it should be noted that the structural composition, characteristics and advantages of the heat exchange device of the present application will be specifically described below by way of example, but all descriptions are for illustration only and do not constitute any limitation to the present application. In this article, the technical terms "first" and "second" are only used for the purpose of distinguishing expressions and are not intended to indicate their order and relative importance. The technical term "connected (or connected, etc.)" covers specific components directly connected to another component and/or indirectly connected to another component, the technical term "substantially" is intended to include insubstantial errors associated with the measurement of a particular quantity, the technical terms "upper", "lower", "top ", "bottom", "inner", "outer" and their derivatives should be related to the orientations in the drawings, unless otherwise specified, the application can adopt multiple alternative orientations.

In addition, for any single technical feature described or implied in the embodiments mentioned herein, the present application still allows any combination or deletion between these technical features (or their equivalents), so as to obtain possible Still other embodiments of the present application not directly mentioned herein. In addition, for the sake of simplifying the drawings, the same or similar parts and features may only be marked at one or several places in the same drawing.

Various embodiments of the heat exchange device, energy transmission device and liquid heating device of the present application are described below by way of example with reference to the accompanying drawings. It should be understood that the present application is not limited thereto. In the respective drawings, the same components are given the same reference numerals.

Those skilled in the art should be able to understand that the heat exchange device of the present application can also use fluids other than water as the working fluid, and can be applied in different scenarios, such as condensing devices in large factories, vehicle devices, refrigeration devices, etc. middle.

In order to improve the efficiency of the energy transmission device in the prior art and reduce its production cost, the first embodiment of the present application provides a heat exchange device. As shown in FIG. 2 , the heat exchange device 1 includes at least a first fluid path for passing the first fluid 35 and a second fluid path for passing the second fluid 36 . The first fluid path and the second fluid path intersect at least two places but are not in fluid communication with each other. At the intersection, the first fluid 35 and the second fluid 36 exchange heat at the intersection, so that at least a part of the first fluid 35 and the second fluid 36 change their state at the same time, such as evaporating from a liquid to a gas or condensing from a gas to liquid. Wherein the first intersection is the first heat exchanger 21 , and the second intersection is the second heat exchanger 31 .

As shown in FIG. 2, in the first fluid path, the working fluid 35 passes through different parts in different states. During this process, the working fluid 35 exhibits different states due to heat absorption or heat release, such as a liquid state. or gaseous.

The structure and function of the first fluid path will be described in detail below in conjunction with the direction of the working fluid 35 . It should be noted that, in order to realize the technical goal of the present application, it is not necessary to include all the components described here. The components introduced here are only for the purpose of exemplary description, and those skilled in the art should be able to increase or decrease the components here, or perform equivalent replacements for individual components according to different application scenarios.

First, as shown in FIG. 3 , the first path in the device of the present application includes a storage chamber 315 for storing a working fluid in a liquid state, that is, a working fluid 35A. The storage chamber 315 is provided with a heater 318 for heating the working fluid 35A to be vaporized into a gaseous working fluid, that is, the working gas 35B. The storage chamber 315 is connected with a fluid channel 326 so that the working gas 35B can pass through it and enter the closed chamber channel 327 in fluid communication therewith. The chamber channel 327 is connected to the compressor 11 , so that the working gas 35B can enter the evaporation section after being compressed by the compressor 11 . At the same time, the storage chamber 315 is also connected to the pump 314 of the working liquid transmission device through a pipeline. The working fluid propulsion device 314 is in fluid communication with the split chamber 316 through a fluid channel 325 for transferring the working fluid 35A from the working fluid storage chamber 315 to the working fluid split chamber 316 through the channel 325 . The working liquid distribution chamber 316 communicates with the inner cavity of the condenser pipe 312A through the distribution hole 317 . The working fluid 35A can enter the inner cavity of the condenser pipe 312A through the diversion hole 317 and flow downwards to finally enter the storage chamber 315 . The working fluid 35A exchanges heat with the outside when passing through the condenser pipe 312A.

Secondly, the compressor 11 located in the first fluid path has an outlet 111 and an inlet 112 , the inlet 112 is in fluid communication with the chamber passage 327 through a pipe, and the outlet 111 is connected to a plurality of working gas passages 211 through a split chamber. The working gas channel 211 is used for passing the working gas 35B and promoting heat exchange between the working gas 35B and the outside. A chamber is provided below the working gas channel 211 for temporarily storing the working liquid 35A formed by condensation after heat exchange, and the chamber sends the working liquid 35A back to the storage chamber 315 through the pipeline and the valve 12 .

Finally, as a preferred embodiment, a working gas propelling device 213 is also provided in the first fluid path, which is used to make the part of the working gas 35B that is not condensed in the working gas channel 211 pass through the The passage 224 enters the working gas passage 211 again and flows through the outer wall of the evaporator pipe 212A, thereby performing heat exchange again. At the same time, the working gas propelling device 213 can also increase the flow velocity of the working gas 35B, so that the working gas 35B accelerates to flow through the outer wall of the evaporator pipe 212A, thereby improving the heat exchange efficiency.

In a preferred embodiment of the present application, when the heat exchange is in progress, the gas valve 222 and the liquid valve 603 are closed, and the first fluid path is formed as a sealed circuit.

As shown in Figure 2, in the second fluid path, the tap water 36 passes through its different parts in different states of matter. During this process, the tap water 36 presents different states of matter, such as liquid or gaseous state, due to heat absorption or heat release. .

The structure and function of the second fluid path will be described in detail below in conjunction with the direction of the tap water 36 . It should be noted that, in order to realize the technical goal of the present application, it is not necessary to include all the components described here. The components introduced here are only for the purpose of exemplary description, and those skilled in the art should be able to increase or decrease the components here, or perform equivalent replacements for individual components according to different application scenarios.

The device of the present application includes a tap water storage chamber 215, which is connected to a tap water source through a valve 601 and a pipe 501 to receive tap water 36A. The tap water storage chamber 215 is provided with a heater 218 for heating the tap water 36A to gasify it, that is, to become water vapor 36B. The storage chamber 215 is connected with a fluid channel 223 so that the water vapor 36B can pass therethrough into the vapor chamber 41 in fluid communication therewith. There is an object to be steamed 411 in the steamed object chamber 41 . The vapor chamber 41 is connected to the water vapor channel 311 through a channel 502 .

The water vapor channel 311 intersects the condenser conduit 312A in the first fluid path, but is not in fluid communication with its lumen, but is fluidly isolated from each other. An exemplary configuration is to arrange a plurality of condenser tubes 312A in the water vapor channel 311 so that the water vapor channel 311 surrounds the plurality of condenser tubes 312A. Preferably, the multiple condenser pipes 312A and the water vapor channels 311 are arranged vertically so as to facilitate the flow of water vapor and working liquid. The water vapor channel 311 is connected to the water vapor propulsion device 313 through a pipe. The water vapor propelling device 313 communicates with the steam chamber 41 through a pipeline, and can push the water vapor 36B that is not condensed in the water vapor passage 311 into the steam chamber 41 through the passage to heat the steam chamber 41 without significantly compressing the water vapor 36B. steam 411, while the excess water vapor 36B enters the water vapor channel 311 again through the channel 502.

At the same time, the tap water storage chamber 215 is also connected to the tap water transmission device 214 through a pipeline. The tap water transmission device 214 is in fluid communication with the tap water distribution chamber 216 through the fluid passage 221 , and is used for transferring the tap water 36A from the tap water storage chamber 215 to the tap water distribution chamber 216 through the passage 221 . The tap water distribution chamber 216 communicates with the inner chamber ( 212 ) of the evaporator pipe 212A through a distribution hole 217 . The tap water 36A can enter the inner cavity of the evaporator pipe 212A through the diversion hole 317 and flow down to finally enter the storage chamber 215 . The tap water 36A exchanges heat with the outside when passing through the evaporator pipe 212A.

The evaporator conduit 212A intersects the working gas channel 211 in the first fluid path, but is not in fluid communication with its lumen, but is fluidly isolated from each other. An exemplary configuration is to arrange a plurality of evaporator pipes 212A in the working gas passage 211 such that the working gas passage 211 includes surrounding the plurality of evaporator pipes 212A. Preferably, the plurality of evaporator pipes 212A and the working gas channels 211 are arranged vertically so as to facilitate the flow of tap water and working gas.

Preferably, the second fluid path also has a distilled water storage chamber 322 in fluid communication with the water vapor channel 311 for collecting condensed distilled water 36C. The distilled water storage chamber 322 is connected with a distilled water pump 604 for pumping the distilled water 36C to the storage chamber 215 and/or 315 through the

valves

602 and 603 respectively.

The present application has described devices above in terms of fluid paths in conjunction with fluid. The structure and working method of the energy exchange device of the present application will be further described in the form of a functional module structure in combination with the structure shown in the accompanying drawings. In an exemplary embodiment, as shown in FIG. 2 , the energy transmission device 1 is a steaming device that heats tap water 36A into steam 36B to heat a steamed object (such as food, etc.) 411 . The energy transmission device 1 includes a compressor 11 , a regulating valve 12 , an evaporation heat exchanger 21 , a condensation heat exchanger 31 , a vapor chamber 41 and several fluid delivery pipes. Wherein, the compressor 11 has an outlet 111 and an inlet 112 , and the regulating valve 12 has an outlet 121 and an inlet 122 . The evaporative heat exchanger 21 is used to exchange heat between the tap water 36A and the working gas 35B flowing through it in a fluid channel that is not connected to each other, so that the tap water 36A is evaporated into water vapor 36B while the working gas 35B in another fluid channel is condensed 35A is the working fluid. The condensing heat exchanger 31 is used to exchange heat between the water vapor 36B and the working liquid 35A flowing through it in the fluid channels that are not connected to each other, so that the water vapor 36B is condensed into distilled water 36C, and the working liquid 35A absorbs the water vapor 36B. The heat becomes working gas 35B. Valve 222 can be selectively closed or opened as desired. The steamed object chamber 41 is an exemplary application scenario, for example, it can be used to place an object to be steamed 411 . Exemplarily, the energy transmission device 1 uses water vapor and liquid water (such as pure water) as working fluids, hereinafter referred to as working liquid 35A and working gas 35B.

The evaporative heat exchanger 21 has a plurality of working gas passages 211 , a plurality of evaporator pipes 212A, a tap water storage chamber 215 , a tap water distribution chamber 216 , a tap water transmission device 214 , a heating device 218 and a working gas propulsion device 213 . Wherein, the evaporation pipe 212A is made of a good heat conductor such as metal, and is used for passing the tap water 36A (and water vapor 36B). Evaporation duct 212A is arranged in a substantially vertical form and has a uniform circular section along its length. The working gas channel 211 is used for the passage of the working gas 35B (and the working liquid 35A) therein, and is arranged to respectively surround each evaporator pipe 212A. The working gas inlet device (such as a blower) 213 is used to promote the flow of the working gas 35B.

The condensing heat exchanger 31 has a plurality of water vapor channels 311 , a plurality of condenser pipes 312A, a working liquid storage chamber 315 , a working liquid distribution chamber 316 , a working liquid transmission device 314 , a heating device 318 and a water vapor propulsion device 313 . The condenser pipe 312A is also made of a good heat conductor such as metal, and is used for passing the working liquid 35A (and the working gas 35B) therein. Condensation duct 312A is arranged in a substantially vertical form and has a uniform circular section along its length. The water vapor passage 311 is used for passing the water vapor 36B (and the distilled water 36C) therein, and is arranged to respectively surround each condenser pipe 312A. A water vapor propelling device (such as a blower) 313 is used to promote the flow of water vapor 36B.

As shown in Figure 3, when the valve 222 and the valve 603 are closed, the plurality of working gas passages 211 in the evaporation heat exchanger 21, the working gas propulsion device 213, the regulating valve 12, and the plurality of condensation in the condensation heat exchanger 31 The inner cavity (312) of the pipeline 312A, the working fluid storage chamber 315, the working fluid distribution chamber 316, the working fluid transmission device (such as a water pump) 314 and the compressor 11 are connected in a sealed form through the sealed pipeline and the sealed chamber to form a closed A circuit for the working gas 35B and the working liquid 35A to flow therein.

The closed circuit is divided into an evaporation section (first channel) and a condensation section (second channel) with the compressor 11 and the regulating valve 12 as boundaries. Specifically, the evaporation section is formed between the compressor outlet 111 in the closed circuit and the inlet 122 of the regulating valve, which includes a plurality of gas passages 211 and working gas pushing devices 213; and the regulating valve outlet 121 and compressor inlet of the closed circuit A condensation section is formed between 112, which includes an inner chamber (312) of a condenser pipe 312A, a working fluid storage chamber 315, a working fluid distribution chamber 316 and a working fluid transmission device 314.

Referring back to FIG. 2 , the tap water storage chamber 215 is connected to a tap water source through a pipe 501 to receive tap water 36A. When in use, the tap water enters the tap water storage chamber 215 through the pipe 501 by opening the valve 601 . At this time, the entire vaporizer 1 is at room temperature, and the closed loop contains working liquid 35A at ambient room temperature and a small amount of working gas 35B at room temperature.

Before the steaming device 1 starts to heat the steamed object 411 with steam, the steaming device 1 must be preheated. This warm-up procedure includes:

1) Start the heater 318 , the working liquid transmission device 314 (such as a water pump), the working gas propulsion device 213 (such as a propeller), and open the valve 222 . The working fluid 35A in the working fluid storage chamber 315 is heated by the heater 318 until boiling. It should be noted that when the device is set up for the first time, an appropriate amount of pure water 35A must be injected into the working fluid storage chamber 315 at one time to be used as the working fluid. Since valve 222 is now open, the circuit is open to atmosphere. If the atmospheric pressure is 1 BAR at that time, the working fluid 35A in the working fluid storage chamber 315 boils at 99.6° C. and generates the working gas 35B (eg, water vapor) at 99.6° C. The working gas 35B enters the closed loop space formed when the valve 222 is closed, and exhausts the air in the space along with a small amount of the working gas 35B.

2) Turn on the heater 218 to heat the tap water 36A in the tap water storage chamber 215 to 99.6°C until it boils and generates water vapor 36B at 99.6°C.

3) After a short period of time, the working gas 35B will completely discharge the air in the circuit through the valve 222. At this time, only the working liquid 35A at 99.6°C and the working gas 35B at 99.6°C exist in the circuit.

At this time, the valve 222 can be closed to form the above-mentioned closed loop, and at the same time, the heater 318 is turned off and the power of the heater 218 is reduced and the compressor 11 is started.

As shown in Figure 3, the compressor 11 in operation pushes and compresses the working gas 35B in the closed circuit from its inlet 112 to its outlet 111, and the regulating valve 12 restricts or regulates the working liquid 35A and the working gas 35B in the closed circuit. in the flow. So since:

1) The pressure in the condensing section is reduced to slightly lower than 1 BAR (eg 0.9 BAR) and the boiling point of the working liquid 35A therein is thus lowered to slightly lower than 99.6°C (eg 96.7°C). The working liquid 35A in the working liquid storage chamber 315 in the condensing section, whose original temperature is 99.6°C, boils due to the lowering of the boiling point due to the depressurization in the condensing section, and a small part of the working liquid 35A evaporates into the working gas 35B at 96.7°C, and evaporates At this time, it takes away latent heat from the working fluid 35A, and lowers the temperature of the working fluid 35A to 96.7°C.

2) The pressure in the evaporating section increases to slightly higher than 1BAR (such as 1.1BAR), and the condensation temperature of the working gas 35B in it also rises to slightly higher than 99.6°C (in one embodiment, its condensation temperature rises to 102.3 ℃), a small part of the working gas 35B in the evaporating section condenses into working liquid beads due to the increase in pressure, and the latent heat released during condensation makes the remaining working gas 35B in the evaporating section heat up to 102.3°C, and the condensed working liquid is also condensed The temperature was raised to 102.3°C. The condensed working liquid 35A with a temperature of 102.3° C. collects at the bottom of the evaporation section and enters the condensation section through the regulating valve 12 . After entering the condensation section, the working fluid 35A at 102.3°C boils due to pressure drop and cools down to 96.7°C.

Therefore, the working compressor 11 and regulating valve 12 maintain the temperature and condensation temperature of the working gas 35B flowing in the evaporating section at 102.3°C by adjusting the air pressure, and at the same time make the working liquid 35A flowing in the condensing section maintain its temperature. The temperature and boiling point are at 96.7°C.

The heat exchange process in the evaporative heat exchanger 21 will be explained below with reference to FIGS. 2 and 3 .

As shown in Figure 2, in the evaporative heat exchanger 21, the tap water propelling device 214 transfers the tap water 36A with a temperature and a boiling point of 99.6° C. from the tap water storage chamber 215 to the tap water distribution chamber 216 located on the upper part of the evaporator pipe 212A through the channel 221 , and enter the inner cavity (212) of the tap water pipeline 212A through the tap water distribution hole 217. The tap water 36A is accelerated to flow downward in the inner cavity of the evaporator pipe 212A due to its own weight. Because tap water distributing channel 217 is narrower than evaporator pipeline 212A inner cavity, the flow of tap water 36A can not be full of all inner cavities of evaporator pipeline 212A, and it is attached to vaporizer pipeline 212A inner wall and flows down and enters tap water storage chamber 215 again, and by The tap water delivery device 214 recirculates into the evaporator pipe 212A.

During this period, the 99.6°C tap water 36A flowing downward in the evaporator pipe 212A absorbs heat from the 102.3°C working gas 35B flowing in the working gas passage 211, thereby being vaporized into 99.6°C water vapor 36B, and at the same time, a part of the working gas 35B is also condensed into the working liquid 35A at 102.3°C due to the heat absorbed. The 99.6°C water vapor 36B formed in the evaporator pipe 212A flows down to the tap water storage chamber 215 following the tap water 36A, and it enters the steamer chamber 41 through the channel 223 to heat the object 411 to be steamed, and the excess water vapor 36B is communicated to the condensation through the channel 502 Heat exchanger 31, and enter its water vapor channel 311.

The working fluid 35A condensed in the working gas channel 211 is collected at the lower part of the evaporating heat exchanger 21 , and enters the working fluid storage chamber 315 in the condensing heat exchanger 31 through the regulating valve 12 .

The heat exchange process in the condensation heat exchanger 31 will be explained below with reference to FIGS. 2 and 3 .

In the condensing heat exchanger 31, the working liquid propelling device 314 transports the working liquid 35A with a temperature and a boiling point of 96.7°C from the working liquid storage chamber 315 through the channel 325 to the working liquid distribution chamber 316 located on the upper part of the condenser pipe 312A, and The working liquid enters the inner chamber (312) of the condenser pipe 312A through the distribution hole 317. The working fluid 35A flows downward in the inner cavity of the condenser pipe 312A due to its own weight. Since the working liquid distribution channel 317 is narrower than the inner cavity of the condenser pipe 312A, the flow of the working liquid 35A will not fill the entire inner cavity of the condenser pipe 312A, and it will flow down the inner wall of the condenser pipe 312A and enter the working liquid again. storage chamber 315, and is recirculated into the condenser pipe 312A by the working liquid transmission device 314.

During this period, the 96.7°C working liquid 35A flowing downward in the condenser pipe 312A absorbs heat from the 99.6°C water vapor 36B passing through the water vapor passage 311, and is vaporized into a 96.7°C working gas 35B, and water vapor 36B is also condensed into distilled water 36C at 99.6°C because of the heat absorbed. The distilled water 36C is collected and stored in the distilled water storage chamber 322 .

The working gas 35B formed in the condenser pipe 312A flows down to the working liquid storage chamber 315 together with the working liquid 35A, and is transported to the compressor 11 through the passage 326 and the chamber passage 327, and is then compressed by the compressor 11 and enters the Evaporate the section and start another cycle.

After cooking for a period of time, the tap water 36A in the tap water storage chamber 215 will gradually decrease due to evaporation. At this time, the valve 602 can be opened and the distilled water pump 604 can be started to transfer the stored distilled water 36C to the tap water storage chamber 215, thereby saving water. .

When cooking is complete, all heating devices, fluid propulsion devices and compressors as shown in Figure 3 will be turned off. As the device cools down gradually, the working gas 35B in the closed loop condenses into the working liquid 35A, and the pressure in the closed loop drops gradually. In one embodiment of the present application, at this point, to balance the pressure in the circuit with atmospheric pressure, valve 222 may be opened to allow air to enter the circuit. And when the device cools down to room temperature, the valve 222 can be closed again to reduce the loss of the working fluid 35A. This configuration method of the present application can make the internal and external air pressure of the entire device basically the same when it is not in operation, and will not cause its components to bear additional air pressure, thereby prolonging the service life of the device and reducing maintenance costs.

As mentioned above, since each preheating process will discharge a small amount of working gas 35B when the air in the device is removed, the working liquid 35A in the working liquid storage chamber 315 will decrease after repeated cooking. At this time, the valve 603 and the distilled water transmission device (such as a water pump) 604 can be turned on to transmit the distilled water 36C into the working fluid storage chamber 315 so as to supplement the lost working fluid 35A. When an appropriate amount of working fluid 35A is contained in the working fluid storage chamber 315, the valve 603 and the distilled water delivery device 604 can be closed again to form a closed circuit.

As shown in FIG. 4A , in the evaporative heat exchanger 21 , the working gas 35B and the tap water 36A respectively contact and exchange heat through the inner and outer walls of the evaporator pipe 212A. As described in the Background Art section, the fine working liquid beads 35C first condense and adhere to the outer wall of the evaporator pipe 212, while the fine water vapor bubbles 36D are first formed and adhere to the inner wall of the evaporator pipe 212A. The fine working liquid beads 35C on the outer wall of the evaporator pipe 212A are poor heat conductors, which reduce the partial contact area between the working gas 35B and the outer wall of the evaporator pipe 212A, thereby reducing the attachment of the working gas 35B to the evaporation through the evaporator pipe 212A wall. The tap water 36A flowing down the inner wall of the pipe 212A directly outputs heat energy (ie latent heat).

Similarly, the tiny water vapor bubbles 36D formed and attached to the inner wall of the evaporator pipe 212A are also poor thermal conductors, which reduce the partial contact area between the tap water 36A flowing on the inner wall of the evaporator pipe 212A and the inner wall of the evaporator pipe 212A, thereby reducing The tap water 36A flowing along the inner wall of the evaporator pipe 212A absorbs heat energy directly from the working gas 36B.

In view of the above, in order to improve the heat exchange efficiency, an embodiment of the present application provides a flow guide structure inside and outside the evaporator pipe 212A shown in FIG. 2 and FIG. 3 . Specifically, as shown in FIG. 4B , an embodiment of the present application is provided with a working gas guide structure 219 in the working gas passage 211. The working gas guide structure 219 includes a portion extending helically adjacent to and around the outer wall of the evaporator pipe 212A. The working gas 35B flowing in the working gas channel 211 flows around the evaporator pipe 212A due to being blocked by the working gas guide structure 219, and drives the tiny working liquid beads 35C to rotate around the evaporator pipe 212A, so that the tiny working liquid The liquid beads 35C are accelerated away from the outer wall of the evaporator pipe 212A due to the centrifugal force, so that the heat exchange effect is significantly improved. Specifically, the working principle here is that the working gas 35B is arranged to flow spirally around the evaporator pipe 212A, so that it drives the small working liquid beads 35C that condense and adhere to the outer wall of the evaporator pipe 212A to spiral around the evaporator pipe 212A. flow. Since the density of the working liquid beads 35C is much higher than that of the working gas 35B, the working liquid beads 35C spirally flowing around the evaporator pipe 212A leave the outer wall of the evaporator pipe 212A due to centrifugal force, thereby allowing more working gas 35B to directly contact the evaporator The outer wall of the pipe 212A greatly speeds up the heat conduction and heat exchange between the working gas 35B and the tap water 36A flowing downward along the inner wall of the evaporator pipe 212A, increases the amount of output heat energy (potential energy), and increases the heat exchange efficiency.

In another embodiment of the present application, an appropriate moving device (not shown in FIG. 4B ) is added to make the working gas guide structure 219 move relative to the evaporator pipe 212A, such as moving up and down along the evaporator pipe 212A or around the evaporator pipe. 212A rotates to more efficiently remove condensation beads attached to the pipe walls. Specifically, when the moving device moves the flow guide structure 219, the part of the working gas flow guide structure adjacent to the outer wall of the evaporator pipe 212A collects the working liquid beads 35C condensed on the outer wall of the evaporator pipe 212A into the working gas guide flow. structure 219, or scrape it off, so that the outer wall of the evaporator pipe 212A has more area to directly contact the working gas 35B, and at the same time, the working liquid beads 35C collected on the working gas guide structure 219 will converge into a larger volume The working liquid beads 35D are easily driven by the spirally flowing working gas 35B to leave the outer wall of the evaporator pipe 212A.

In a preferred embodiment of the present application, a fluid propelling device such as a working gas propelling device 213 is provided in the evaporating section, as shown in FIG. Part of the working gas 35B passes through the channel 224 and passes through the outer wall of the evaporator pipe 212A again. The working gas propelling device 213 can also accelerate the working gas 35B to flow through the outer wall of the evaporator pipe 212A to promote heat exchange.

In another preferred embodiment of the present application, the fluid propelling device 213 is used in conjunction with the aforementioned working gas guide structure 219 to accelerate the spirally flowing working gas 35B, so that the working liquid beads 35C condensed on the outer wall of the evaporator pipe 212A And 35D leaves the outer wall of steamer pipeline 212A faster.

Another preferred embodiment of the present application is provided with a spiral guide device in the evaporating section, for example, the tap water distribution hole 217 is set so that when the tap water 36A flows out of the distribution hole 217, it flows into the evaporator pipe 212A One side of the shaft core flows, so that the tap water 36A flowing downward in the evaporator pipe 212A flows spirally in the evaporator pipe 212A, so as to drive the fine water vapor bubbles 36D formed on the inner wall of the evaporator pipe 212A around the shaft core of the evaporator pipe 212A spiral flow. Because the density of tap water 36A is much higher than the density of water vapor bubbles 36D, therefore, the tap water 36A of spiral flow flows close to the inner wall of evaporator pipe 212A due to centrifugal force, and this flow mode is easy to form the water formed on the inner wall of evaporator pipe 212A. The steam bubbles 36D are directed toward the center of the evaporator pipe 212A, so that the water vapor bubbles 36D are more likely to leave the inner wall of the evaporator pipe 212A. In this way, the tap water 36A can directly contact more inner wall area of the evaporator pipe 212A, that is, the heat exchange area is greatly increased, thereby greatly promoting the heat exchange effect.

A further embodiment of the present application provides a tap water diversion structure 220 disposed in the evaporator pipe 212A, as shown in FIG. 4B , for enhancing the spiral flow of the tap water 36A in the evaporator pipe 212A. The flow guiding structure 220 includes a portion adjacent to the inner wall of the evaporator pipe 212A and spirally extending around the axis of the evaporator pipe 212A. The tap water 36A flowing in the evaporator pipe 212A is affected by the tap water guide structure 220 to speed up the rotation speed, which advantageously drives the fine water vapor bubbles 36D to rotate around the axis of the evaporator pipe 212A at a faster speed. This makes the fine water vapor bubbles 36D leave the inner wall of the evaporator pipe 212A faster, so as to improve the heat exchange effect.

In another embodiment of the present application, an appropriate moving device (not shown in FIG. 4B ) is added to move the tap water guide structure 220 relative to the evaporator pipe 212A, for example, up and down along the evaporator pipe 212A. Move or rotate around the axis of the evaporator pipe 212A. When the mobile device is moving, the part of the tap water flow guide structure adjacent to the inner wall of the evaporator pipe 212A will move the air bubbles 36D formed on the inner wall of the evaporator pipe 212A, and collect these air bubbles on the tap water flow guide structure 220 and converge into a larger Large volume of water vapor bubbles 36E. Larger bubbles are more likely to be driven by the spirally flowing tap water 36A and leave the inner wall of the evaporator pipe 212A faster, so that the tap water 36A contacts more with the inner wall of the evaporator pipe 212A and absorbs heat energy from the working gas 35B more effectively.

In the heat exchange device shown in FIG. 2 and FIG. 3 , in addition to the heat exchanger 21 , there is also a heat exchange efficiency problem at the heat exchanger 31 . As shown in FIG. 5A , the condenser tube 312A has an outer wall and an inner wall, and the water vapor 36B and the working fluid 35A respectively contact the inner and outer walls and exchange heat through the inner and outer walls. For the same reason as above, fine distilled water droplets 36F will condense and adhere to the outer wall of the condenser pipe 312A, while fine working gas bubbles 35E will form and adhere to the inner wall of the condenser pipe 312A. Since the fine distilled water droplets 36F condensed and attached to the outer wall of the condenser pipe 312A are poor thermal conductors, it reduces the partial contact area between the water vapor 36B and the outer wall of the condenser pipe 312A, thereby reducing the contact area between the water vapor 36B and the water along the condenser pipe. The heat exchange effect between the working liquid 35A flowing downward on the inner wall of 312A.

Similarly, the working gas bubbles 35E formed on the inner wall of the condenser pipe 312A are poor thermal conductors, which also reduce the partial contact area between the working liquid 35A flowing on the inner wall of the condenser pipe 312A and the inner wall of the condenser pipe 312A, thereby reducing the The heat exchange effect between the working liquid 35A flowing on the inner wall of the condenser pipe 312A and the water vapor 36B.

In view of the above, in order to improve the heat exchange efficiency, an embodiment of the present application provides a flow guide structure inside and outside the condenser pipe 312A shown in FIG. 2 and FIG. 3 . Specifically, in one embodiment of the present application, a water vapor guiding structure 319 is provided in the water vapor channel 311 , as shown in FIG. 5B , for promoting the spiral flow of the water vapor 36B in the water vapor channel 311 . The water vapor guiding structure 319 includes a portion extending helically adjacent to and around the outer wall of the condenser tube 312A. The water vapor 36B flowing in the water vapor channel 311 is affected by the water vapor guide structure 319 and flows spirally around the condenser pipe 312A, thereby driving the fine distilled water droplets 36F to rotate around the condenser pipe 312A. This can make the fine distilled water droplets 36F leave the outer wall of the condenser pipe 312A faster, so as to improve the heat exchange effect.

Its working principle is as follows: make the water vapor 36B flow spirally around the condenser pipe 312A, which can drive the condensed and attached fine distilled water droplets 36F to flow spirally around the condenser pipe 312A. Since the density of the distilled water beads 36F is much higher than that of the water vapor 36B, the distilled water beads 36F flowing spirally around the condenser pipe 312A leave the outer wall of the condenser pipe 312A due to centrifugal force, thereby allowing more water vapor 36B to directly contact the outer wall of the condenser pipe 312A, thereby The water vapor 36B is facilitated to export thermal energy (potential energy) in a conductive manner to the working liquid 35A flowing down the inner wall of the condenser tube 312A.

In another embodiment of the present application, an appropriate moving device (not shown in FIG. 5B ) is added so that the water vapor guide structure 319 moves relative to the condenser pipe 312A, such as moving up and down along the condenser pipe 312A or around The condensation pipe 312A rotates, so as to more efficiently remove the condensation water droplets attached to the pipe wall. Specifically, when the moving device makes the water vapor guiding structure 319 move, the water vapor guiding structure part adjacent to the outer wall of the condenser pipe 312A will condense and collect the distilled water drops 36F attached to the outer wall of the condenser pipe 312A. The water vapor diversion structure 319, so that the outer wall of the condenser pipe 312A has more area to directly contact the water vapor 36B, and at the same time, the distilled water droplets 36F collected on the water vapor diversion structure 319 will merge into a larger volume of distilled water droplets 36G , which is easily driven by the spirally flowing water vapor 36B to leave the outer wall of the condenser pipe 312A.

In a preferred embodiment of the present application, a fluid propelling device such as a water vapor propelling device 313 is provided in the condensation heat exchanger 31, as shown in FIG. The condensed water vapor 36B passes through the channel 327 and then passes through the steam chamber 41 to heat the object 411 to be steamed, while the excess water vapor 36B enters the water vapor channel 311 again through the channel 502 . The water vapor propelling device 313 accelerates the water vapor 36B to flow through the outer wall of the condenser tube 312A to facilitate heat exchange.

In another preferred embodiment of the present application, the steam propulsion device 313 is used in conjunction with the aforementioned steam guide structure 319, and the steam 36B that accelerates the spiral flow is more helpful to promote the distilled water attached to the outer wall of the condenser pipe 312A

Beads

36F and 36G leave the outer wall of condenser tube 312A faster.

In another preferred embodiment of the present application, a spiral guide device is provided in the condensation section, for example, the working liquid distribution hole 317 is arranged so that when the working liquid 35A flows out of the distribution hole 317, it flows toward the condenser One side of the shaft core of the pipe 312A flows, so that the downwardly flowing working liquid 35A spirals through the condenser pipe 312A, so as to drive the fine working gas bubbles 35E formed on the inner wall of the condenser pipe 312A to spiral around the condenser pipe 312A shaft core flow. Since the working liquid 35A has a much higher density than the working gas bubbles 35E, the spirally flowing working liquid 35A clings to the inner wall of the condenser pipe 312A due to centrifugal force, and brings the working gas bubbles 35E formed on the inner wall of the condenser pipe 312A to the condenser Central direction of pipe 312A. This makes it easier for the working gas bubbles 35E to leave the inner wall of the condenser duct 312A. In this way, the working liquid 35A can directly contact more inner wall area of the condenser pipe 312A, that is, the heat exchange area is greatly increased, thereby greatly promoting the heat exchange effect.

A further embodiment of the present application provides a working liquid flow guide structure 320 disposed in the condenser pipe 312A, as shown in FIG. 5B , for enhancing the spiral flow of the working liquid 35A in the condenser pipe 312A. The working liquid flow guide structure 320 includes a part that is adjacent to the inner wall of the condenser pipe 312A and spirally extends around the axis of the condenser pipe 312A. The working water 35A flowing in the condenser pipe 312A is accelerated by the influence of the working liquid guide structure 320, thereby driving the tiny working gas bubbles 35E to rotate around the axis of the condenser pipe at a faster speed. This enables the fine working gas bubbles 35E to leave the inner wall of the condenser pipe 312A faster, so as to improve the heat exchange effect.

In another embodiment of the present application, an appropriate moving device (not shown in FIG. 5B ) is added to move the working fluid guide structure 320 relative to the condenser pipe 312A, such as moving up and down along the condenser pipe 312A. Or rotate around the condenser pipeline 312A. When the moving device moves, the working liquid guide structure part adjacent to the inner wall of the condenser pipe 312A moves the working gas bubbles 35E formed on the inner wall of the condenser pipe 312A, and collects them on the working liquid guide structure 320 And converge into a larger volume of working gas bubbles 35F. Since larger bubbles are more likely to be driven away from the inner wall of the condenser pipe 312A by the spirally flowing working liquid 35A, the working liquid 35A will more contact the inner wall of the condenser pipe 312A and absorb heat energy from the water vapor 36B more effectively.

It should be understood that, in the above-mentioned energy transmission device taking the steam device 1 as an example, the working liquid 35A in the sealed circuit absorbs heat from the external (outside the sealed circuit) water vapor 36B in the condensing heat exchanger 31 during steaming. Turn into working gas 35B and make external water vapor 36B condense into distilled water 36C; Simultaneously, when steaming, working gas 35B in the sealed circuit outputs heat to external tap water 36A in evaporative heat exchanger 21 and self-condenses into working liquid 35A and The external tap water 36A is vaporized into water vapor 35B. It should be understood that the energy transmission device of the present invention is not limited to the steam device, and it can also be used in other applications where heat exchange exists.

Alternative Embodiment 1 of the present application provides a heat exchanger (21, 31), which is used to condense a first gas (35B, 36B) into a first condensate (35A, 36C), and convert a second liquid ( 36A, 35A) is gasified into a second gas (36B, 35B), which includes a first gas passage (211, 311) for passing the first gas therein and at least one first pipe (212A, 212A, 312A), wherein, the first gas flows through the outer wall of the first pipeline, the second liquid flows through the inner wall of the first pipeline, and the first gas channel has a first gas that promotes the helical flow of the first gas around the outer wall of the first pipeline. A gas flow guiding structure (219, 319). Preferably, at least a part of the first gas flow guiding structure is disposed around and adjacent to the outer wall of the first pipe; wherein, when the heat exchanger is used, the first gas flow guiding structure moves relative to the first pipe. Preferably, wherein, the first pipeline has a second liquid guiding structure (220, 320) that promotes the spiral flow of the second liquid in the first pipeline; wherein, the second liquid guiding structure surrounds the The shaft core of the first pipe is helically arranged and at least a part thereof is adjacent to the inner wall of the first pipe; wherein, when the heat exchanger is used, the second liquid guiding structure moves relative to the first pipe.

Alternative embodiment 2 of the present application provides an energy transmission device (1) using the heat exchanger (21) of alternative embodiment 1 as a first heat exchanger, the device comprising: a compressor (11), It has an inlet (112) and an outlet (111); a regulating valve (12), which has an inlet (122) and an outlet (121); and a second heat exchanger (31), which includes at least one second pipe with an inner wall (312A), the first condensate flows through its inner wall; and the first condensate transmission device (314), which is used to transmit the first condensate, wherein, the compressor, the regulating valve, the second pipeline lumen , the first condensate transmission device and the first gas channel form a closed circuit for the first gas and the first condensate to flow in it; wherein, the first gas channel is located between the compressor outlet and the regulating valve inlet in the closed circuit Between, the inner chamber of the second pipeline and the first condensate transmission device are located between the outlet of the regulating valve and the inlet of the compressor; wherein, the compressor is used to compress the first gas entering it from its inlet and promote the The first gas flows toward its outlet; wherein, the regulating valve is used to regulate the flow of the first gas and the first condensate in the closed circuit; wherein the second heat exchanger is used to make the first condensate The liquid absorbs heat from the outside (outside the closed circuit) and is vaporized into the first gas; wherein, when in use, the first condensate transmission device makes the first condensate in the closed circuit at the outlet of the regulating valve and compressed Flow through the inner wall of the second pipe (312A) multiple times between the inlets of the heat exchanger, wherein the energy transmission device is used to make the first gas that absorbs heat from the outside in the second heat exchanger transfer its heat to the first heat exchanger Give the second liquid. Preferably, the energy transmission device is characterized in that the second pipeline has a first condensate flow guide structure (319) that promotes the helical flow of the first condensate in the second pipeline. Preferably, in the energy transmission device, the first condensate diversion structure is helically arranged around the axis of the second pipeline and at least a part of it is adjacent to the inner wall of the second pipeline; wherein, when using the energy transmission When installed, the first condensate guiding structure moves relative to the second pipeline.

Alternative Embodiment 3 of the present application provides an energy transmission device (1) using the heat exchanger (21) of Alternative Embodiment 1 as a first heat exchanger, which includes: a compressor (11), which having an inlet (112) and an outlet (111); and a regulating valve (12) having an inlet (122) and an outlet (121); and a first gas propulsion device (213) to facilitate the flow of the first gas, and a second A heat exchanger (31), which includes at least one second pipe (312A) having an inner wall, through which the first condensate flows; wherein, the compressor, the regulating valve, the inner cavity of the second pipe, the first The gas propelling device and the first gas channel form a closed circuit for the first gas and the first condensate to flow in it; wherein, the first gas propelling device and the first gas channel are located between the compressor outlet and the closed circuit Between the inlet of the regulating valve, the second pipeline lumen is located between the outlet of the regulating valve and the inlet of the compressor; wherein, the compressor is used to compress the first gas entering it from its inlet and promote the flow of the first gas to it Outlet flow; wherein, the regulating valve is used to regulate the flow of the first gas and the first condensate in the closed circuit; wherein, the second exchanger is used to make the first condensate flow from the outside (closed circuit) other than) absorbing heat and gasifying into the first gas; wherein, the first gas propelling device is set so that a small part of the first gas flows through the first gas several times between the compressor outlet and the regulating valve inlet in a closed circuit The outer wall of the pipeline, wherein the energy transmission device is used to make the first gas that absorbs heat from the outside in the second heat exchanger transfer its heat to the second liquid in the first heat exchanger. Preferably, the second gas formed in said first heat exchanger is introduced into a second heat exchanger, where it condenses and transfers its heat to the first condensate.

Alternative Embodiment 4 of the present application provides an energy transmission device (1) using the heat exchanger (21) of Alternative Embodiment 1 as a first heat exchanger, which includes: a compressor (11), which having an inlet (112) and an outlet (111); and a regulating valve (12) having an inlet (122) and an outlet (121); a (first) valve (222) which can be selectively closed or opened and a second a heat exchanger (31) comprising at least one second pipe (312A) having an inner wall, wherein said first condensate flows through its inner wall; wherein, when said (first) valve is closed, said compression The device, the regulating valve, the inner cavity of the second pipeline and the first gas passage form a closed circuit for the flow of the first gas and the first condensate; wherein, the first gas passage is located between the compressor outlet and the regulating valve inlet in the closed circuit Between, the inner chamber of the second pipeline is located between the outlet of the regulating valve and the inlet of the compressor; wherein the compressor is used to compress the first gas entering it from the inlet and promote the flow of the first gas to the outlet; wherein , the regulating valve is used to regulate the flow of the first gas and the first condensate in the closed circuit; wherein, the second heat exchanger is used to absorb the first condensate from the outside (outside the closed circuit) Heat and vaporize into the first gas. Wherein, the energy transmission device is used to transfer the heat of the first gas, which absorbs heat from the outside in the second heat exchanger, to the second liquid in the first heat exchanger, wherein, when the (first) valve When opened, the first gas channel and the inner cavity of the second pipeline communicate with the outside world. Preferably, the energy transmission device further comprises a heating device (318) for heating the first condensate or the first gas; wherein, when the heater device is activated, the (first) valve is in an open state. Preferably, the second gas formed in the first heat exchanger is introduced into the second heat exchanger, where it is condensed into a second condensate (36C) and transfers its heat to the second heat exchanger A condensate. Preferably, the energy transmission device further includes a second valve (603), which can be selectively closed or opened, wherein, when the second valve is open, it allows the second condensate to enter the first The closed loop is formed when the valve is closed; wherein, when the second valve is closed, it forms the closed loop together with the closed first valve.

Alternative Embodiment 5 of the present application provides an energy transmission device (1) using the heat exchanger (31) of Alternative Embodiment 1 as a first heat exchanger, the device comprising: a compressor (11), It has an inlet (112) and an outlet (111): and a regulating valve (12), which has an inlet (122) and an outlet (121); and a second heat exchanger (21), which includes at least one second gas channel ( 211) for the passage of the second gas; and a second liquid transfer device (314), which is used to transfer the second liquid, wherein the compressor, the regulating valve, the first pipeline lumen, and the second liquid transfer device and the second gas channel form a closed circuit for the second gas and the second liquid to flow in it; wherein, the second gas channel is located between the compressor outlet and the regulating valve inlet in the closed circuit, and the first pipeline the chamber and the second liquid transfer means are located between the outlet of the regulator valve and the inlet of the compressor; wherein the compressor is adapted to compress the second gas entering it from the inlet thereof and to facilitate the flow of the second gas to the outlet thereof; wherein , the regulating valve is used to regulate the flow of the second gas and the second liquid in the closed circuit; wherein, the second heat exchanger is used to make the second gas output heat to the outside (outside the closed circuit) And condense into the second liquid; wherein, the second liquid transmission device is used to make the second liquid flow through the inner wall of the first pipeline multiple times in the closed circuit between the outlet of the regulating valve and the inlet of the compressor, wherein The energy transmission device is used to make the second gas that absorbs heat from the first gas and the first condensate in the first heat exchanger transfer its heat to the outside in the second heat exchanger. Preferably, the energy transfer device further comprises: a second gas transfer device for facilitating the second gas to pass through the second gas channel multiple times in the closed circuit between the compressor outlet and the regulating valve inlet. Preferably, the second heat exchanger is arranged such that the first liquid (36A) absorbs heat from the second gas and is vaporized into the first gas, wherein the first gas formed in the second heat exchanger is It is introduced into the first heat exchanger to be condensed into the first condensate.

Alternative Embodiment 6 of the present application provides an energy transmission device (1) using the heat exchanger (31) of Alternative Embodiment 1 as a first heat exchanger, which includes: a compressor (11), It has an inlet (112) and an outlet (111); and a regulating valve (12), which has an inlet (122) and an outlet (121); and a (first) valve (222), which can be selectively closed or opened; and a second heat exchanger (21), which includes at least one second gas channel (211) for the passage of the second gas; wherein, when the (first) valve is closed, the compressor, the regulating valve, the second A pipeline lumen and a second gas channel form a closed circuit for the flow of the second gas and the second liquid; wherein, the second gas channel is located between the compressor outlet and the regulating valve inlet in the closed circuit; the first The inner cavity of the pipeline is located between the outlet of the regulating valve and the inlet of the compressor, wherein the compressor is used to compress the second gas entering it from the inlet and promote the flow of the second gas to the outlet; wherein the regulating valve is used In regulating the flow of the second gas and the second liquid in the closed circuit; wherein, the second heat exchanger is used to condense the second gas into the second liquid and transfer its heat to the outside (outside the closed circuit) . Wherein, when the (first) valve is opened, the second gas channel and the inner cavity of the first pipeline communicate with the outside; wherein, the energy transmission device is used to make the first heat exchanger transfer from the first The second gas that absorbs heat from the gas and the first condensate transfers its heat to the outside through the second heat exchanger. Preferably, the energy transfer device further comprises heating means (318) for heating the second liquid or the second gas, wherein when the heating means is activated, the (first) valve is in an open state. Preferably, the second heat exchanger is arranged such that the first liquid (36A) absorbs heat from the second gas and is vaporized into the first gas, wherein the first gas formed in the second heat exchanger is It is introduced into the first heat exchanger to be condensed into the first condensate. Preferably, the energy transmission device further includes: a second valve (603), which can be selectively closed or opened, wherein, when the second valve is opened, it allows the first condensate to enter and when the first valve is closed In the closed circuit formed when the second valve is closed; wherein, when the second valve is closed, it forms the closed circuit together with the closed first valve.

The above descriptions are only preferred embodiments of the application, and are not intended to limit the application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the application shall be included in the scope of the application. within the scope of protection.

Claims

A heat exchange device comprising a first fluid path for a first fluid (35A, 35B) in the first fluid path and a second fluid (36A, 36B) outside the first fluid path ), the first fluid path is divided into a first channel and a second channel,

Wherein, at least a part of the first channel is formed as a part of the first heat exchanger (21), so as to make the first fluid (35B) in the gaseous state flow through the first heat exchanger (21 ), at least a part of the second channel forms a part of the second heat exchanger (31), so that the first fluid (35A) flowing therein in a liquid state absorbs heat energy,

Wherein, the first channel and the second channel are configured to have different air pressure values when the heat exchange device is in operation,

Wherein, the first fluid path is sealed when it is in the heat exchange working state,

Wherein, the first heat exchanger (21) is provided with a first gas guide structure ( 219), wherein, the second heat exchanger (31) is provided with a first liquid guide for promoting the spiral flow of the first fluid (35A) in the liquid state in the second heat exchanger (31) stream structure (320),

Wherein at least one of the first gas guiding structure (219) and the first liquid guiding structure (320) is movable.
The heat exchange device according to claim 1, wherein the first fluid path is at the first heat exchanger (21) and the second heat exchanger (31) and outside the first fluid path The second fluid path intersects in a manner not in fluid communication with each other, the heat exchange device being configured such that:

The gaseous first fluid (35B) exchanges heat with the liquid second fluid (36A) in the second fluid path when flowing through the first heat exchanger (21), so that the liquid second fluid (36A) is vaporized into said second fluid (36B) in gaseous state and at least a portion of said first fluid in gaseous state (35B) is condensed into said first fluid (35A) in liquid state;

The liquid first fluid (35A) exchanges heat with the gaseous second fluid (36B) in the second fluid path when flowing through the second heat exchanger (31), so that the liquid At least a portion of said first fluid (35A) is vaporized into said first fluid (35B) in gaseous state and at least a portion of said second fluid (36B) in gaseous state is condensed into said second fluid in liquid state ( 36C).
The heat exchange device according to claim 2, wherein at least a part of the first liquid guide structure (320) is adjacent to the inner wall of the second channel forming the second heat exchanger (31) and along the The inner wall is formed with a spiral flow guide channel, wherein at least a part of the first gas guide structure (219) is adjacent to the outer wall of the second fluid path in the first heat exchanger (21) and along the The outer wall is formed with a helical guide channel.
The heat exchange device according to any one of the preceding claims, further comprising a compressor (11) arranged in the first fluid path and a regulating valve (12) spaced apart from the compressor (11), The first fluid path is divided into the first passage and the second passage by the compressor (11) and the regulating valve (12), wherein the compressor (11) and the regulating valve (12) For changing the air pressure in the first channel and the second channel so that the first channel and the second channel have different air pressure values when the heat exchange device is in operation.
The heat exchange device according to any one of the preceding claims, further comprising a first gas for promoting the gaseous first fluid to circulate in the first passage through the first heat exchanger (21) Power unit (213).
The heat exchange device according to any one of the preceding claims, further comprising a first liquid for promoting the circulation of the first fluid in the liquid state through the second heat exchanger (31) in the second channel power unit (314).
The heat exchange device according to any one of the preceding claims, wherein the first fluid path can be fluidly communicated with the outside by selectively opening the gas valve (222) and/or the liquid valve (603).
The heat exchange device according to claim 7, further comprising a first heating device (318) and a first chamber (315) located on the first fluid path, wherein the first chamber (315) is used The liquid-state first fluid (35A) is accommodated, wherein the first heating device is used to heat the first chamber (315) to vaporize the first fluid (35) therein.
The heat exchange device according to claim 8, wherein when the first heating device is used to heat the first chamber (315), the gas valve (222) is in an open state.
The heat exchange device according to claim 7, further comprising a second chamber (322) for collecting and containing the second fluid (36C) liquefied through the second heat exchanger, the liquefied The second fluid can enter the first chamber (315) by opening the liquid valve (603).
A heat exchange device for exchanging heat between a first fluid (35/36) and a second fluid (36/35) in a different state of matter from said first fluid prior to the heat exchange, said heat The exchange device has a first heat exchange channel (211/311) for passing the first fluid and a second heat exchange channel (212/312) for passing the second fluid, wherein the second The heat exchange channel (212/312) intersects and passes through the first heat exchange channel (211/311) in a manner not in fluid communication with each other, wherein the The first heat exchange channel (211/311) is provided with a first flow guide structure that promotes the spiral flow of the first fluid (35/36) flowing through the first heat exchange channel around the second heat exchange channel (219/319), wherein said second heat exchange channel (212/312) is provided with a device to facilitate said second fluid (36/35) flowing through said second heat exchange channel in said second heat exchange a second flow guide structure (220/320) for spiral flow in the channel, at least one of said first flow guide structure (219/319) and said second flow guide structure (220/320) being movable, Wherein at least a part of the first fluid and at least a part of the second fluid change state due to the heat exchange.
The heat exchange device according to claim 11, wherein at least a part of the first flow guide structure (219/319) is adjacent to the outer wall of the second heat exchange channel (212/312) and formed along the outer wall There are spiral guide channels.
The heat exchange device according to claim 11 or 12, wherein at least a part of the second flow guide structure (220/320) is adjacent to the inner wall of the second heat exchange channel (212/312) and along the The inner wall is formed with a helical guide channel.
The heat exchange device according to any one of claims 11-13, further having a first fluid path through which a first fluid flows, said first fluid path having a compressor disposed in said first fluid path (11) and a regulating valve (12) spaced apart from the compressor (11), the first fluid path is divided into a first channel and a second channel by the compressor (11) and the regulating valve (12). Two channels, wherein the first fluid path is sealed when it is in the heat exchange working state, the compressor (11) and the regulating valve (12) are used to change the first channel and the second channel so that the first channel and the second channel have different air pressure values when the heat exchange device is in operation, wherein the first heat exchange channel (211) is composed of at least a part of the first channel form.
The heat exchange device of claim 14, further comprising said second fluid path through which a second fluid flows, said second fluid path being located outside said first fluid path and connected to said first fluid path Intersecting in a manner that is not in fluid communication with each other, wherein the second heat exchange channel (212) is formed by at least a portion of the second fluid path.
The heat exchange device according to claim 15, wherein at least a part of the second channel of the first fluid path forms a third heat exchange channel (312), and the second fluid path is in contact with the first fluid A fourth heat exchange channel (311) is formed at the intersection of the third heat exchange channel (312) of the path, and the third heat exchange channel (312) is not in fluid communication with each other with the fourth heat exchange channel (311) intersect and pass through the fourth heat exchange channel (311).
The heat exchange device according to claim 16, wherein the third heat exchange channel (312) is provided with a third flow guide structure (320) for promoting the spiral flow of the first fluid therein, and the fourth heat exchange channel (312) The exchange channel (311) is provided with a fourth flow guide structure (319) for promoting the spiral flow of the second fluid therein, wherein the third flow guide structure (320) and the fourth flow guide structure (319) At least one is movable, wherein the first fluid and the second fluid exchange heat through the third heat channel and the fourth heat channel and at least a portion of the first fluid and the second fluid At least a portion of the fluid changes state.
The heat exchange device according to claim 17, wherein at least a part of the fourth flow guide structure (319) is adjacent to the outer wall of the third heat exchange channel (312) and a spiral shape is formed along the outer wall. Diversion channel.
The heat exchanging device according to claim 17, wherein at least a part of the third flow guide structure (320) is adjacent to the inner wall of the third heat exchanging channel (312) and has a spiral shape along the inner wall. Diversion channel.
The heat exchange device according to any one of claims 14-19, further comprising means for promoting circulation of the gaseous first fluid in the first channel through the first heat exchange channel (211) A first gas power unit (213).
The heat exchange device according to any one of claims 16-20, further comprising means for promoting circulation of said first fluid in liquid state through said third heat exchange channel (312) in said second channel A first hydrodynamic device (314).
The heat exchange device according to any one of claims 14-21, wherein the first fluid path can be fluidly communicated with the outside by selectively opening the gas valve (222) and/or the liquid valve (603).
The heat exchange device according to any one of claims 14-22, further comprising a first heating device (318) and a first chamber (315) located on the first fluid path, wherein the first The chamber (315) is used to accommodate the liquid first fluid (35A), wherein the first heating device is used to heat the first chamber (315) to vaporize the first fluid (35A) therein ).
The heat exchange device according to claim 23, wherein when the first heating device is used to heat the first chamber (315), the gas valve (222) is in an open state.
The heat exchange device according to claim 23, wherein at least a part of the gaseous second fluid (36B) is condensed into the liquid second fluid (36C) when passing through the fourth heat exchange channel (311) ), wherein the heat exchanging device further includes a second chamber (322) for collecting and containing the condensed second fluid, and the condensed second fluid can be obtained by opening the liquid valve (603) into the first chamber (315).